Refrigerant compressor



Nov. 20, 1962 R. N. RIGNEY REFRIGERANT COMPRESSOR 6 Sheets-Sheet l FiledNov. 28, 1960 INVENTOR. M /G/VE/ L7/CHAP@ Nov. 20, 1962 R. N. RIGNEYREFRIGERANT COMPRESSOR 6 Sheets-Sheet 2 Filed Nov. 28. 1960 INVENTOR.704,420 M /G/z/Ey www Nov. 20, 1962 R. N. RIGNEY 3,064,449

REFRIGERANT COMPRESSOR Filed Nov. 28. leso e sheets-sheet s 5 76JNVENTOR. 4Q/acme@ M leben/Ey rrae/l/grs.

Nov. 20, 1962 R. N. RIGNEY REFRIGERANT COMPRESSOR 6 Sheecs-Sheecl 4Filed Nov. 28, 1960 INVEN TOR.

Afro/@Mfrs Nov. 20, 1962 R. N. RIGNEY REFRIGERANT COMPRESSOR 6Sheets-Sheet 5 Filed NOV. 28, 1960 lm/ENTOR.

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Nov. 20, 1962 R. N. RIGNEY 3,064,449

REFRIGERANT COMPRESSOR Filed Nov. 28, leso 6 Sheets-Sheet 6 INVENTOR.

' ten Patented Nov. 20, 1962 fornia Filed Nov. 28, 19h41, Ser. No.72,093 21 Caims. CL 62-476) This invention relates generally torefrigeration systems, and more particularly refrigerant compression insuch systems, the invention being characterized in the provision of anovel and improved motor-driven comressor unit, as well as in thecombination of such a unit in a refrigerant system.

It is a general object of the invention to provide a novel compressorand motor unit in which iluid lubricant is contained and becomesentrained in flowing refrigerant during compressor operation, the motorand compressor unit incorporating separator means operable to separatethe lubricant from the compressed refrigerant prior to flow of thelatter from the motor-compressor unit to condenser means in the system,thereby preventing excessive accumulation of lubricant in therefrigerant flowing to the condenser. It is also an important object lof the invention to utilize the compressed refrigerant for cooling theelectric motor driving the compressor, such cooling being accomplishedin a particularly advantageous and novel manner through theincorporation of passages within the motor-rotor structure Within whichthe compressed refrigerant is flowable in heat transfer relation withthe motor-rotor structure, these passages presenting very littleobstruction to the flow of compressed refrigerant. At the same time, therotor structure forming the passages is operable to effect centrifugalseparation of the uid lubricant from the compressed refrigerant as thelatter tlows through the motor in cooling relation therewith, all aswill be described.

The invention is also characterized in the combination of the elementsmaking up the motor-driven compressor assembly, these elements includinga manifold, an electric motor and rotary compressor/ means locatedbetween the motor and manifold and rotatable by the motor forcompressing the refrigerant. This assembly contains passages for flowingcirculating refrigerant through the manifold to the compressor means tobe compressed thereby, these passages also acting to return thecompressed refrigerant to the manifold to be circulated outside theassembly for cooling and to be returned in compressed and cooled stateto the manifold. In addition, the assembly contains other passages forreceiving the compressed and cooled refrigerant returned to the manifoldfrom outside the assembly for flowing refrigerant through the manifoldand compressor means to the motor in cooling relation therewith and forreturning the refrigerant from the motor back through the compressormeans to the manifold for circulation therefrom into the refrigeratingsystem outside the assembly. As will be seen, maximum utilization ofavailable space to provide for flow of the refrigerant Within theassembly to accomplish these functions is made possible by locating themanifold, compressor means, and motor in relationships described and tobe described.

These other features and objects of the invention, as Well as thedetails of an illustrative embodiment, will be more fully understoodfrom the following detailed description of the drawings in which:

FIG. 1 is a schematic showing of a refrigeration system incorporatingthe invention;

FIG. 2 is an enlarged elevation taken in section through themotor-driven compressor assembly;

FG. 3 is a section taken on line 3 3 of FIG. 2;

FIG. 4 is a section taken on line 4 4 of FIG. 2;

FIG. 5 is a View like FIG. 4, showing elements of the compressor rotatedwith respect to the positions of these same elements shown in FIG. 4;

FIG., 6 is a section, partly broken away, taken on line 6 6 of FIG. 2;

FIG. 7 is a section taken on line 7 7 of FIG. 2;

FIG. 8 is a section taken on line 8 8 of FIG. 2;

FIG. 9 is a section taken on line 9 9 of FIG. 3;

FIG. l0 is an exploded perspective showing of the basic elements of themotor-driven compressor assembly shown in det-ail in FIG. 2; and,

FG. 11 is a schematic showing of the circulation of refrigerant throughthe motor-driven compressor elements illustrated in block form.

Referring first to FIG. 1, a particular refrigeration systemincorporating the invention is shown to include a motor-drivencompressor assembly generally designated at 10, the latter including amanifold 11 having connected therewith a refrigerant delivery or exhaustduct 12, a refrigerant return or suction duct 13, and other refrigerantoutlet and inlet ducts 14 and 15, the functions of which will be laterdescribed. The assembly 10 also is shown in FIG. 1 as incorporating apair of housings 16, which will be understood as joined to oppositefaces of the manifold, so that the housings extend endwise oppositelyfrom the manifold.

Tracing through the circulation of refrigerant Within the system, thesupply refrigerant, typically but not necessarily comprising Freon 12,passes through duct 12 to and is delivered at 13 to a receiver 19. Fromthe latter the liquiiied refrigerant passes through a heat exchanger 29,an expansion valve 21 and then through an evaporator 22. After passingthrough the latter, the refrigerant is returned at 23 through the heatexchanger 20 and then returned as suction gas through the duct 13 to thecompressor assembly 10. i

It will also be observed in FIG. 1 that super-heated compressed Freon orrefrigerant is circulated from the outlet duct 14 through a pre-coolerunit indicated at 24, the purpose of which is to cool the Freon,removing its super-heat so that the cooled, compressed Freon may becirculated back through the inlet duct 15 into the assembly 11) forcooling the motor, as will be further described. Typically, but notnecessarily, the superheated and compressed Freon discharged from theunit 10 through the duct 14 has a temperature around 230 F. and thecooled Freon is returned through the duct 15 at a temperature of aroundF. After passing in cooling relation with the motor in the assembly 1t),the compressed Freon is exhausted to the system through duct 12 at atemperature of around 187 F. These temperatures are merely illustrativeof typical operating conditions, and are not to be taken as limiting theoperating temperatures of the present or equivalent systems or units.

Referring now to FIGURES l0 and 11 for a broad understanding of thearrangement and operation of the motor, compressor and manifold elementsof the compressor assembly, it will be seen from FIG. 1l that a pair ofcompressor units 25 are located at opposite sides of the centralmanifold 11 and two electric motors 26 are placed or located endwiseoutwardly of the compressors 25, the elements 11, 25 and 26 thus beingarranged in stacked series relation, the advantages of which will appearfrom the following description.

As broadly conceived, such advantages include the enablement of adequatecooling of the high output compressor and motor units by the compressedrefrigerant, which is distributed or circulated to the compressor andmotor units from the central manifold 11. Thus, as schematically shownin FIG. 11, suction gas or refrigerant is supplied to the manifold 11,as indicated at 13, and is then distributed at 27 to the compressors 25.Thereafter, the compressed and superheated refrigerant is returned backto the manifold 11 as indicated by the lines 28 for external circulationat 14 to the pre-cooler which is shown in FIG. 1 at 24. The return ow ofcooled compressed refrigerant is supplied at 15 to the manifold and isthen led or conducted through the compressors to the motors 26, asindicated by the lines 29. The circulating-compressed refrigerant isthen returned at 39 back through the compressors 25, typically throughthe tubular drive shafts therefor, to the central manifold 11, fromwhich the refrigerant was circulated at 12 to the external refrigerationsystem as previously described. Since the coolant comprises therefrigerant itself, and since the elements 11, 25 and 26 are arranged asdescribed, a very compact compressor assembly is provided with anextremely high output to weight ratio.

Now referring to FIG. 2, the assembly 16 is shown to include theopposite casings or housings 16 having flanges bolted to the oppositefaces 31 of manifold block 11,

Vthe bolts being shown at 32. Extending the description to FIGS. V3, 7,8 and l0, the manifold chamber is shown to include a ring 33 forming acavity 34 through which access of lubricant between opposite sides orfaces of the manifold chamber may be had, the lubricant normally partlyfilling the interiors of the casings or housings 1 and the cavity 34 ofthe manifold chamber. v

Located centrally within the chamber 34 is a block 35 containing a bore36, which is in communication with an outlet or exhaust refrigerantfitting 37 through a duct or passage 38. The latter is formed by legstructure 39 integral with the body and the manifoldrchamber ring 33, asbetter shown in FIG. 3 and FIG. 7. The bore 36 also-receives the tubularcoaxial extents 40 of end plates 41VV for the compressor bodies 42,these bodies and end plates being part of the compressors 25. Thetubular extents 40 in turn receive the end extents of hollow shafts 43,which are coaxially mounted by suitable roller bearings 44?, space 45remaining between the ends of the shafts 43 and bearing retainers 46 toprovide a path 45 for exhaust iiow from within the shafts 43 throughspace 45 and the passage 38 to the exterior refrigerant system.

Also, integral with the manifold chamber is leg structure 47 forming apassage 48 through which suction refrigerant gas flows after enteringthe manifold fitting 49. Such flow then passes at 48 to the inlet 50within the body 35 ofY theV manifold, as seen in FIG. 8. The inlet 5t)communicates between opposite faces 51 of the block 35 and furthermoreregisters with inlets 52 in the end l plates 41 and with inlets 53 inthe compressor body 42, as'seen in FIGS. 4 and 5.

Themanifold also includes leg structure 54 forming a-passage 55 throughwhich compressed and superheated refrigerant flows from the compressorchamber to the exterior fitting 56, the latter communicating with duct14, asshown in FIG. l. Compressed and superheated refrigerant leaves thedischarge passage 5.7 within the compressor block, as seen in FIGS. 4, 5and 9, and is delivered past a reed valve 58 into a passage 59 withinthe manifold and communicating with the passage 55.

Finally, the manifold includes integral leg structure 60 formingv apassage 61, which communicates between the exterior fitting. 62 and apassage 63 for receiving cornpressed and precooled refrigerant fordelivery to the compressor and motor. Passage 63 is in registration withpassages 64 and 65 within the compressor end plate 41 and the compressorbody 42.

Referring now to the compressor unit, as illustrated in FIGS..4 and 5,the body 42 thereof forms a cylindrical bore 66 through which the shaft43 extends axially, with respectto the axis 67. Acylindrical piston 63of smaller diameter than the bore 66 is arranged to rotate about theboreV 66 and eccentrically with respect to the axis 67 as by mountingthepiston upon an eccentric 69 carried by the shaft 43, there beingneedle bearings 70 between the cylindrical surface of the eccentric andthe bore 71 of the piston 68. Such rolling contact of the piston withthe bore 66 of the compressor body, all in response to shaft rotation inthe direction of the arrow 72, serves to draw suction refrigerant gasthrough the entrance port 53 into the clearance space 73 between thepiston and the bore, which space is then progressively closed or reducedin volume between the rolling line of contact 74 of the piston 68 withbore 66, and the line of engagement 174 between the piston surface andthe lip 75 of a follower 76 spring urged into contact with the pistonsurface. It is clear from FIGS. 4 and 5 that the entrance ports 53 is atone side of the follower 76 and the discharge port 57 is at the oppositeside of the follower. Also, communication between space 73 and inletport 53 is inter'- iupted once the line of contact 74 has moved past theport 53 in a clockwise sense. Accordingly, the pressure within theclearance space 73 and within the delivery port or passage 57 increasesas the piston rolls around the bore 66 until such pressure increase issuicient to open the reed valve 53, as viewed in FIG. 9. At such timethe compressed and super-heated refrigerant escapes through the manifoldto the external line 14, as viewedV in FIG. l and FIG. 6, intermittentdelivery occurring once per revolution of the shaft. Delivery pressurealsoV escapes through a valve 78 at the opposite end of the compressorfor return to passage 59, valve 78 typically but not necessarily beingmounted on end plate 79 of the compressor structure. Y l

Returning to the description of the follower 76, it is shown in FIGS. 2,4 and 5 to be urged toward the piston 68 by a series of compressionsprings Sii the opposite ends of which are received within suitableopenings 8-1 and 82 formed within the body 42 and the follower 76.

Turning now to the description of the electric motors for rotating thecompressors, reference to FIGS. 2, 6 and l0 will show each -motor 26 toinclude a housing 84, which is bolt-connected to the manifold block 35by bolts shown at passing through the compressor blocks from the motorhousing flange `86. Carried within each -housing 84 is a stator assembly87 that includes laminations 38 through which extent suitable windings,the end turns of which appear at 89. Mounted for rotation within thestator annulus is a rotary assembly generally indicated at 90, the rotorincluding annular laminations 91 and end rings 92 and 93, al1 of whichare included within the squirrel cage construction of the rotor, thesquirrel cage lbars of which appear externally at 94.

The rotor annulus is made integral with the shaft 43 by means of supportvanes 95 arranged in spiral convolutions, each vane convolutioncomprising a series of radial spokes 96 having polygonal cross-sectionsin planes normal to the spoke radii.

Accordingly, axially spiraling passages 97 are formed between thesuccessive vane convolutions, and the spokes' form radial protuberancesprojecting into these passages, as typified by the sides 98 and edges 99of the vanes, all for the purpose of. creating turbulant flow ofpre-cooled compressed refrigerant passing through the passages 97,thereby promoting heat transfer. The latter is necessary to cool therotor structure, and it is furthermore found that the precooledrefrigerant passes through the gap v100 formed betwen the rotorlaminations and stator laminations 88 for cooling purposes.

Such pre-cooled refrigerant enters the passages 97 between the spiralconvolutions 95 from an entrance chamber 101 which communicates with thepassage 65 in the compressor body as shown in FIG. 9, through acorresponding passage 102 in the compressor end plate 79 as viewed in.FIG. 9. The compressed refrigerant after passing through the passages 97iiows radially inwardly toward ports 103 in the tubular shaft 43 nearthe extreme end of the shaft and thereafter the refrigerant ows backthrough the shaft bore 104, and` th-us through the motor and compressorto discharge at 45 and 38, as previously described.

An additional and important function of the spiral vane convolutions 95is to centrifuge outwardly the uid lubricant which becomes entrainedwithin the refrigerant flowing through the compressor. Such entrainmentand distribution of the lubricant as a mist for lubricating thebearings, as for example those shown at 105, 70 and 44,

is of course desirable; however, separation of the lubricant from thecompressed refrigerant just prior to delivery thereof to the externalsystem is also desired in order not to affect adversely the operation ofthe latter system. Accordingly, adjacent spokes of the vanes form radialgrooves for collecting and centrifugally impelling the lubricantoutwardly against the inner bore 166 of the rotor laminations 91, suchthrowout being opposite in direction to the inward tlow of therefrigerant toward and into the ports 103, thereby accomplishingseparation of the refrigerant just prior to exit delivery thereof.Furthermore, the liquid lubricant so separated flows through holes orports 167 appearing in FIG. 6 in the rotor end plate 198, and thelubricant is thus returned to the sump 159 for-med between the housingS4 and the casing 16. The lubricant from the sump works its way backinto the system of passages within the compressor and motor via thefollower, as indicated by the arrows '110, and it will be understoodthat other slight clearances allow return flow of lubricant into thecirculating refrigerant. In this connection, FIG. 2 illustrates anannularly discontinuous O-ring 112 sealing off between a flange 113 onthe motor housing 84 and casing 16.

Brieiiy, referring now to the overall operation of the compressorassembly, the suction refrigerant enters the manifold through thefitting 49 and through passage 48 and entrance ports 53, 51 and 52 fordelivery to the compressor piston. Rotation of the latter carries therefrigerant around the clearance passage 73 and discharges therefrigerant under pressure at 57 for exit delivery past valve 58 andinto passages 59 and 55. Thereafter, refrigerant circulates externallyin the system through lines 14 and 15 for pre-cooling.

Upon return to the manifold the refrigerant enters through the inlettting 62, FlG. 3, and through passage 61, to the passage 63, from whencethe refrigerant flows endwise through the compressor passages 64, 65 and102 for delivery to the passages 101 and 97 within the motor. Therein,the pre-cooled and compressed refrigerant cools the motor structurewhile lubricant is being separated from the refrigerant, whereupon thecleaned refrigerant exits through the ports 103 into the shaft bore 194to flow back through the motor and compressor units to the manifold.Finally, the refrigerant is delivered through passages 45 and 33 forexternal circulation, as described in connection with FIG. 1 lines 12,13, 18 and 23.

I claim:

l. For combination in a refrigeration system in which refrigerant iscycled through condenser and evaporator means, an assembly includingiluid lubricated motor driven compressor means operable to receivereturn ow of refrigenant from the evaporator means and to pressurize therefrigerant for supply to the condenser means, said assembly containingpassage means in which fluid lubricant becomes entrained in -owingrefrigerant during compressor operation, said assembly includingseparator means supporting motor rotor structure outwardly of theseparator and inwardly of `motor stator structure and being operable toclean the compressed refrigerant by centrifugally separating lubricanttherefrom prior to compressed refrigerant ilow to the condenser means,thereby to prevent excessive accumulation of lubricant in therefrigerant flowing to the condenser.

2. For combination in a refrigeration system in which refrigerant iscycled through condenser and evaporator means, an assembly including amotor and uid lubricated compressor means operable lby the motor toreceive return ow of refrigerant from the evaporator means and topressurize refrigerant for supply to the condenser means, said assemblycontaining passage means in which uid lubricant becomes entrained inowing refrigerant during compressor operation, said passage meansincluding motor driven rotary passage extent within which therefrigerant has turbulent ow proximate the motor to absorb heat producedby operation of said motor, and separator means operable to clean thecompressed refrigerant by centrifugally separating lubricant therefromprior to compressed refrigerant ow to the condenser means, thereby toprevent excessive accumulation of lubricant in the refrigerant owing tothe condenser.

3. The invention as defined in the claim 2 in which said assembly hasfirst inlet and outlet ports communicating with the compressor forpassing said return flow of refrigerant to the compressor and forpassing the compressed and superheated refrigerant stream to saidcondenser means to precool the compressed refrigerant stream, and saidassembly has second inlet and outlet ports for passing said precooledrefrigerant stream to said passage means and separator means and forpassing the cleaned refrigerant to the condenser and evaporator means.

4. For combination in a refrigeration system in which refrigerant iscycled through condenser and evaporator means, an assembly including anelectric motor and fluid lubricated rotary piston compressor meansoperable by the motor to receive return flow of refrigerant from theevaporator means and to pressurize refrigerant for supply to thecondenser means, said assembly including a shaft for driving thecompressor rotary piston in response to motor operation, said assemblycontaining passages in which fluid lubricant becomes entrained inflowing refrigerant during compressor operation, said passages includingmotor driven rotary passage extent within Which the refrigerant ingaseous state has turbulent flow proximate the motor to absorb heatproduced by operation of said motor, said assembly including separatormeans mounted in said shaft and operable in response to shaft rotationto clean the compressed refrigerant by centrifuging entrained lubricanttherefrom outwardly away from the shaft prior to compressed refrigerantflow to the condenser means, thereby to prevent excessive accumulationof lubricant in the refrigerant flowing to the condenser, said shafthaving an inlet and a hollow interior for receiving clean compressedrefrigerant flowing from said separator means to said compressor means.

5. The invention, as dened in claim 4, n which the motor rotor andstator are spaced radially outwardly from said shaft and said separatormeans extends intermediate the shaft and motor rotor, whereby lubricantis centrifuged outwardly toward the motor rotor.

6. The invention as dened in claim 5, in which said separator meanscomprises vanes carried by the shaft and circularly spaced thereabout,said vanes being integral with the motor rotor to receive heat byconduction therefrom.

7. The invention as defined in claim 6, in which said vanes haveprotuberances exposed at the vane sides for creating turbulance in thegaseous refrigerant from which lubricant is centrifuged in response tovane rotation, thereby to promote heat transfer from the vanes to therefrigerant.

8. The invention as defined in claim 5 in which said assembly includes amanifold and said compressor includes a chamber receiving the rotarypiston, said mamfold and separator means being at axially opposite endsof said chamber, said manifold and chamber containing refrigerant intakeand discharge ports communicating with the compressor piston.

9. The invention as dened in claim 8 in which said intake and dischargeports are adapted respectively to pass the return flow of refrigerant tothe compressor and to pass the compressed and superheated refrigerantstream to the condenser means to pre-cool the refrigerant stream,

and in which the manifold and compressor chamber have other intake anddischarge ports for passing the precooled refrigerant stream to saidvpassages and separator means and for passing the cleaned Vrefrigerantfrom the interior of said shaft to the condenser andY evaporator means.Y

10. The invention, as defined in claim 8, in which the compressorchamber has a cylindrical bore through which said shaft extends axially,said piston having a cylindrical periphery and being mountedeccentrically on said shaft to rotate eccentrically about the shaft axisin rolling contact with the chamber bore in response to shaft rotation,said intake and discharge ports opening into said bore at circularlyspaced locations and in which said compressor includes a spring urgedfollower projecting through said bore between said locations andengaging the piston' periphery to seal off between the intake anddischarge ports.

11. The invention, as defined in claim 10, in which the chamber containsa radial slotV receiving the follower to move radially in response topiston rotation, said follower having a pressure shoulder facing awayfrom the piston and being in communication with said discharge port.

12. The invention as defined in claim 4 in which said assembly includesa housing enclosing said compressor and motor, said housing containingliquid lubricant in a reservoir outside the motor and compressor, and towhich lubricant entrainment is returnable after separation thereof fromthe refrigerant.

13. For combination in a refrigeration system in which refrigerant viscycled through condenser and evaporator means, an assembly includingamanifold, a pair of electric motors and a pair of iiuid lubricatedrotary piston compressors, the compressorsbeing at opposite sides ofthe' manifold and between the manifold and said motors, the compressorsbeing operable by the motors to receive return' tiow of refrigerant fromthe evaporator means and to pressurize refrigerant for supply to thecondenser means, said assembly including shaftmeans for driving thecompressor rotary' piston in response to motor Voperation, said assemblycontaining passages in which iiuid lubricant becomes entrained inflowing refrigerant during compressor operation, and in which therefrigerant in gaseous state absorbsheat produced by operation of saidmotors, and separator meansmounted on said shaft and operable inresponse to shaftrotation to clean the compressed refrigerant byvcentrifuging entrained lubricant therefrom outwardly away from theshaft means prior to compressed refrigerant iiow to the compressormeans, thereby to prevent excessive accumulationV of lubricant in therefrigerant iiowing to the condenser means, said'shaft means havinginlets anda hollow interior for receiving clean compressed lubricantiowing from said separator meansI to the manifold andthenV to thecompressor and evaporator means.

14. The invention as dened in claim 13 in which each motor rotor andstator is spaced radially outwardly from a shaft and the separator meansincludes vanes extending intermediate the shaft and each motor rotor,whereby lubricant is centrifuged outwardly toward the motor rotors.

@15. The invention as defined in claim 14 in which said separator vanesare carried by the shaft and are integral with the motor rotorsto'r'eceive heat by conduction therefrom.

16. The invention asdeined in claim 13 in which said V- assemblyincludes housing means enclosing said com- 8: pressors and motors, saidhousing means containing liquid lubricant reservoirs outside the motorsand compressors, and means forming passages through which lubricant isreturnable to said reservoirs after lubricant separation from therefrigerant.

17. For combination in a system for transferring heat by circulation ofliuid subject to heating and cooling, an assembly including manifoldmeans, motor means,V and rotary compressor means driven by saidmotor'means for compressing the transfer liuid, said assembly containingpassages for liowing circulating iiuid through the manifold andcompressor means to said motor means in cooling relation therewith andfor returning the iiuid from said motor means back through saidcompressor means to the manifold means to be circulated therefrom and insaid system, said passages including motor driven rotary passage extentwithin which the liuid has turbulent iiow proximate the motor to absorbheat produced by operation of the motor.

18. The invention as defined in claim 17, including liuid lubricantcontained by said assembly, and in which said assembly includesseparator means in the path of transfer fluid circulation for separatinglubricant from theV heat transfer fluid.V

19. For combination in a refrigerant circulating system, an assemblyincluding a manifold, an electric motor, and rotary compressor meansbetween the motor and manifold and Irotatable by the motor forcompressing the refrigerant, said assembly containing first passages forflowing circulating refrigerant through the manifold to the compressormeans to be compressed thereby and for returning the compressedrefrigerant to the manifold to be circulated outside said assembly forcooling and to be returned in compressed and cooled state'to themanifold,

` said assembly containing other passages for receiving the refrigerantreturned to the manifold from outside said assembly, for 'flowing therefrigerant through the manifold and compressor means and the motor incooling relation therewith and for returning the refrigerant from saidmotor back through said compressor means to the manifold to becirculated therefrom into said system outside said assembly, said otherpassages includingmotor driven rotary passage extent within which therefrigerant has turbulent ow proximate the motor to absorb heat producedby operation ofthe motor.

20. The invention as de-ined in claim 19 including uid lubricantlcontained by said assembly; and in which said assembly includes rotaryseparator means driven by said motor in the path of refrigerantcirculation for separating fluid lubricant from the circulatoryrefrigerant.

21. The invention as defined in claim 20 including means connected inseries communication with said first passages for receiving and coolingthe compressed refrigerant to aV temperature lower than the motoroperating temperature prior to return of the compressed refrigerant tosaid other passages.

References Cited in the tile of this patent UNITED STATES PATENTS

